JP4281771B2 - Torque converter stator support device - Google Patents

Description

  The present invention relates to a torque converter provided in a vehicle, and more particularly, to a support structure for a stator provided in the torque converter.

  A torque converter, which is a fluid transmission device that is provided in a power transmission path between a vehicle power source and an automatic transmission, amplifies the torque generated by the power source and transmits the amplified torque to the automatic transmission, has become widespread. Yes. Generally, a torque converter is interposed between a pump impeller that is rotated by a drive source such as an engine, a turbine runner that is rotated by a working fluid sent out by the pump impeller, and a pump impeller and the turbine runner. And a stator. Here, the stator is provided to assist the rotation of the pump impeller by changing the flow direction of the working fluid circulated from the turbine runner to the pump impeller in the same direction as the rotation direction of the pump impeller.

  In order to make such a torque converter compact, for example, in Patent Document 1, a thrust bearing is disposed on the side surface of a one-way clutch that is disposed on the inner periphery of the stator and rotatably supports the stator. In the above, the axial raceway length is shortened by assembling the bearing race of the thrust bearing directly to the outer race of the one-way clutch.

JP 2004-132526 A

  By the way, in the torque converter of Patent Document 1, a key that protrudes inward from the stator is provided to prevent the outer race and the bearing race from rotating, and the outer race and the bearing race are formed with a key groove for fitting with the key. Has been. Here, the key provided in the stator is relatively troublesome to process, and the oil supplied from the outer race oil passage groove passes through the key groove, so that the key groove of the outer race is deepened. As a result, it is difficult to form a key groove by broaching the outer race, which can be carried out relatively easily, and the outer race becomes expensive.

  The present invention has been made against the background of the above circumstances, and an object thereof is to provide an inexpensive stator support device in a torque converter of a type in which a bearing race of a thrust bearing is directly assembled to an outer race. It is in.

In order to achieve the above object, the gist of the invention according to claim 1 is that (a) the outer race of the one-way clutch disposed on the inner periphery of the stator wheel of the torque converter and the outer periphery of the non-rotating member A stator of a torque converter having an inner race of a one-way clutch that is non-rotatably connected, an end bearing that is interposed between the outer race and the inner race, and a bearing race that is disposed on a side surface of the outer race. In the supporting device, (b) the bearing race is supported so as to be rotatable relative to the outer race, (c) a gap is formed between the bearing race and the stator wheel, and (d) A side surface of the bearing race is connected to a lubricating oil hole formed in the end bearing as appropriate. A plurality of ring oil passage holes are formed in the circumferential direction, and the lubricating oil supplied to the bearing oil passage holes has an outer race oil passage groove in which a plurality of bearing oil passage holes are formed in the outer race in the circumferential direction. To the bearing oil passage grooves formed on the outer peripheral portion of the bearing race, and (e) the axial center of the gap formed between the stator wheel and the bearing race. The length in the direction is set to be approximately equal to the groove depth of the outer race oil passage groove .

  According to a second aspect of the present invention, in the stator support device for a torque converter according to the first aspect, the inner peripheral portion of the stator wheel and the outer peripheral portion of the outer race are fitted by press-fitting. The side wall of the stepped portion formed on the outer peripheral portion of the outer race and the side wall of the protruding portion formed radially inward from the inner peripheral surface of the stator wheel are in contact with each other. It is characterized by.

The gist of the invention according to claim 3 is that, in the torque converter support device according to claim 1 or 2, the outer peripheral side of the bearing oil passage hole is formed with a wide hole width in the circumferential direction. It is characterized by.

According to the stator support device of the torque converter of the first aspect of the invention, since the bearing race is not stopped, complicated processing such as providing a key on the stator wheel is not performed, and the manufacturing cost can be suppressed. it can. Further, since the gap is formed between the stator wheel and the bearing race, sliding wear between these relatively rotatable members can be prevented. Even if the bearing race rotates freely, the lubricating oil hole formed in the end bearing and the bearing oil passage hole are always communicated, and the oil passage groove and the bearing race oil passage hole formed in the outer race Is communicated. Further, since the bearing oil passage groove is formed, the oil is supplied into the torque converter through the bearing oil passage groove. As described above, the oil passage hole and the oil passage groove are formed, so that the oil can be stably supplied.

  According to the stator support device for a torque converter of the invention according to claim 2, the side wall of the stepped portion formed on the outer peripheral portion of the outer race and the radially inner side from the inner peripheral surface of the stator wheel. Since the side walls of the formed projections are in contact with each other, when a thrust load in the axial direction is applied to the stator wheel, the thrust load is directly transmitted to the outer race via the contact portion. The thrust load is prevented from being transmitted to the outer periphery of the bearing race. Thereby, the deformation | transformation by the thrust force of the outer peripheral part of a bearing race is blocked | prevented.

According to the stator support device of the torque converter of the invention of claim 3, since the outer peripheral side of the bearing oil passage hole is formed with a wide hole width in the circumferential direction, the bearing oil passage hole and the outer race Regardless of the relative rotational positional relationship between the oil passage grooves, the bearing oil passage holes and the outer race oil passage grooves can always communicate with each other.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a cross-sectional view illustrating a configuration of a torque converter 10 according to an embodiment of the present invention. The torque converter 10 includes a pump impeller 12, a turbine runner 14, a lock-up clutch 16, a one-way clutch 18, and a stator 20.

  The pump impeller 12 is connected to a crankshaft to which an output of an engine or the like (not shown) is transmitted, for example, and rotated around the shaft center at the same rotational speed as the crankshaft, and a plurality of pump impellers 12 in the circumferential direction. When the front case 12a is rotated by driving the engine, the impeller 12c of the pump impeller 12 is rotated integrally with the front case 12a. ing. Then, due to the rotation of the impeller 12c of the pump impeller 12, the hydraulic oil filled in the pump impeller 12 is pushed and rotated by the impeller 12c in the pump impeller 12, and the centrifugal force generated thereby causes the outer peripheral direction. Be driven to. This hydraulic oil collides with the impeller of the turbine runner 14 disposed so as to face the pump impeller 12, and after the impeller of the turbine runner 14 is rotated by the impact force, the impeller of the turbine runner 14 is rotated. It flows along the curve, returns to the pump impeller 12 through the stator 20, and circulates in the torque converter 10.

  When the relative rotational speed difference between the pump impeller 12 and the turbine runner 14 is relatively large, such as when the pump impeller 12 starts rotating, the flow of hydraulic oil flowing out of the turbine runner 14 is reduced to the pump impeller. The stator 20 is provided between the pump impeller 12 and the turbine runner 14 via a one-way clutch 18 that is spline-fitted to a cylindrical fixed shaft 26 that is a non-rotating member. As a result, the flow of the hydraulic oil is converted to a direction that assists the flow of the pump impeller 12 by the impeller 20a of the stator 20. On the other hand, when the rotational speed of the turbine runner 14 is increased and the relative rotational speed difference between the pump impeller 12 and the turbine runner 14 is decreased, the impeller 20a of the stator 20 works to prevent the flow. Since the stator 20 is rotated by 18, such a hindrance to flow is prevented. The turbine runner 14 is connected by a rivet 32 to a turbine hub 30 that is spline-fitted to an input shaft 28 of an automatic transmission (not shown) corresponding to an output shaft. Is transmitted from the input shaft 28 to an automatic transmission (not shown) via the turbine hub 30.

  FIG. 2 is a cross-sectional view of a main part for explaining the stator support device 34 that supports the stator 20 of FIG. 1 via the one-way clutch 18. The stator 20 includes a plurality of impellers 20a arranged in the circumferential direction, and a stator wheel 20b connected to the inner peripheral side of the impeller 20a and integrally rotated, and the inner periphery of the stator wheel 20b. A one-way clutch 18 is disposed on the side. The one-way clutch 18 is connected to the outer race 36 arranged in a state of being fitted in the inner periphery of the stator wheel 20b and the outer periphery of the fixed shaft 26 that is a non-rotating shaft in a non-rotatably fitted state. The race 38, a plurality of sprags 40 held at predetermined intervals in the circumferential direction by a retainer 39 between the outer race 36 and the inner race 38, and between the outer race 36 and the inner race 38, A pair of annular end bearings 42 are provided so as to cover both ends of the sprag 40. Further, a front thrust bearing 46 is interposed in the gap between the turbine hub 30 and the outer race 36, and similarly, a rear thrust bearing 48 is interposed in the gap between the rear case 12 b and the outer race 36. The outer race 36 is supported in the axial direction by the turbine hub 30 and the rear case 12b via front and rear thrust bearings 46 and 48. The stator support device 34 of the present embodiment is mainly composed of these members.

  The front thrust bearing 46 is disposed so as to sandwich the plurality of longitudinal rolling elements 50 disposed in a posture along the radial direction at a predetermined interval in the circumferential direction and the plurality of rolling elements 50. A pair of disk-shaped first front races 52 and second front races 54 are included, and the first front race 52 is provided between the rolling element 50 and the turbine hub 30. A second front race 54 is interposed between the outer race 36 and the outer race 36 so as to be relatively rotatable.

  The rear thrust bearing 48 is disposed so as to sandwich a plurality of longitudinal rolling elements 56 disposed at predetermined intervals in the circumferential direction and in a posture along the radial direction, and the plurality of rolling elements 56. A pair of disk-shaped first and second rear races 58 and 60 are included, and the first rear race 58 is provided between the rolling element 56 and the rear case 12b. The second rear race 60 is interposed between the two rear races 60 so as to be relatively rotatable. A plurality of outer race oil passage grooves 67 penetrating in a radial direction, which will be described later, are formed in a circumferential direction on a surface of the outer race 36 that is in close contact with the second rear race 60. Note that the second rear race 60 of the present embodiment corresponds to the bearing race of the present invention.

  The inner peripheral portion of the inner race 38 is spline-fitted to the end portion of the fixed shaft 26 that is a non-rotating member, and is always stopped from rotating. Serrations are formed on the outer peripheral surface 62 of the outer race 36, and the outer race 36 is integrally rotated by being fitted into the stator wheel 20b by serration press fitting, which is a known technique. In addition, a stepped portion 64 is formed on the outer peripheral portion of the outer race 36, and an annular stopper 66 that protrudes radially inward from the inner peripheral surface is formed on the inner peripheral surface of the stator wheel 20b. Yes. Here, when the outer race 38 and the stator wheel 20b are press-fitted, the side wall of the stepped portion 64 and the side wall of the stopper 66 are press-fitted until they are brought into contact with each other. The serration press-fitting of the present embodiment corresponds to the press-fitting of the present invention, and the stopper 66 corresponds to the protruding portion of the present invention.

  Here, when the axial load acting on the stator case 20b toward the rear case 12b is applied to the stator wheel 20b by the hydraulic oil in the torque converter 10, the thrust load is stepped from the stopper 66 of the stator wheel 20b to the step of the outer race 36. It is transmitted to the outer race 36 via the part 64. The thrust load transmitted to the outer race 36 is supported by a rear thrust bearing 48. Thus, the thrust load is not transmitted from the outer peripheral portion of the second rear race 60 to the rear thrust bearing 48, and deformation of the outer peripheral portion of the second rear race 60 is prevented.

  The second front race 54 of the front thrust bearing 46 can be rotated in the circumferential direction by being fitted in close contact with the outer race 36 along the side wall of the inner race 38, the side wall of the end bearing 42, and the side wall of the outer race 36. It is supported. Further, the outer peripheral edge of the second front race 54 is in contact with a snap ring 68 fitted to the inner peripheral surface of the stator wheel 20b, so that the second front race 54 and the stator wheel 20b are relatively aligned in the axial direction. Movement is blocked. Similarly, the second rear race 60 of the rear thrust bearing 48 is fitted into the inner side of the stator wheel 20b in close contact with the side wall of the inner race 38, the side wall of the end bearing 42, and the side wall of the outer race 36. The outer peripheral edge of the second rear race 60 is abutted against a snap ring 70 fitted to the inner peripheral surface of the stator wheel 20b, so that the second rear race 60 and the stator wheel 20b are supported. Relative movement in the axial direction is prevented. In the second front race 54, a plurality of bearing oil passage holes 71 are formed in the circumferential direction so as to communicate with a lubricating oil hole 73 penetrating the end bearing 42 as appropriate. Further, the second rear race 60 is formed with a plurality of bearing oil passage holes 72 in the circumferential direction which communicate with the lubricating oil holes 73 formed in the end bearing 42 as appropriate. Further, a plurality of notched bearing oil passage grooves 74 are formed in the outer peripheral portion of the second rear race 60 in the circumferential direction.

  Here, a gap 75 in the axial direction is formed between the outer peripheral portion of the second rear race 60 and the inner peripheral portion of the stator wheel 20b. The gap 75 is press-fitted until the stopper 66 of the stator wheel 20b and the stepped portion 64 of the outer race 36 come into contact with each other, and when the second rear race 60 and the outer race 36 are in close contact with each other, the stator wheel 20b and the second rear race are in contact. The distance between the outer race 36 and the outer race oil passage groove 67 is approximately equal to the groove depth of the outer race 36. The gap 75 prevents sliding contact between the second rear race 60 and the stator wheel 20b, and forms an oil passage. Since the stator wheel 20b is made of an aluminum member, the sliding contact with the second rear race 60 is prevented, thereby preventing the durability of the stator wheel 20b from being deteriorated due to aluminum wear. Since the outer race 36 is made of a steel material such as bearing steel having excellent wear resistance, sliding wear between the outer race 36 and the second rear race 60 can be minimized by sliding the outer race 36 and the second rear race 60 together. To suppress.

  A gap 77 is formed between the outer periphery of the second front race 54 and the inner periphery of the stator wheel 20b. The gap 77 is press-fitted until the stopper 66 of the stator wheel 20 b and the stepped portion 64 of the outer race 36 come into contact with each other, and the outer peripheral edge of the second front race 54 is formed in contact with the snap ring 68. Is set to The gap 77 prevents the second front race 54 and the stator wheel 20b from sliding. Since the stator wheel 20b is formed of an aluminum member, the sliding contact with the second front race 54 is prevented, so that a decrease in the durability of the stator wheel 20b due to aluminum wear is prevented. Since the outer race 36 is made of a steel material such as bearing steel having excellent wear resistance, sliding wear between the outer race 36 and the second front race 54 can be minimized by sliding the outer race 36 and the second front race 54 together. To the limit.

  FIG. 3 is a front view for explaining the shape of the second rear race 60 of FIG. 3 corresponds to an arrow view of the second rear race 60 viewed from the direction of arrow A in FIG. The second rear race 60 is made of, for example, bearing steel having excellent wear resistance and has a disk shape. In the second rear race 60, a plurality of T-shaped bearing oil passage holes 72 are formed at equal angular intervals (12 in this embodiment) in the circumferential direction. Further, a plurality of bearing oil passage grooves 74 that are notched in an arc shape are formed on the outer peripheral portion at equal angular intervals (12 in this embodiment). The bearing oil passage hole 72 is supplied with oil from a lubricating oil hole 73 formed in the end bearing 42.

  FIG. 4 is a layout diagram showing a positional relationship among the stator wheel 20b, the second rear race 60, the outer race 36, and the snap ring 70, and corresponds to a view as seen from an arrow A in FIG. In FIG. 4, the inner peripheral end of the bearing oil passage hole 72 formed in a T shape in the second rear race 60 indicated by the one-dot chain line is the lubricating oil hole 73 formed in the end bearing 42 and their relative rotational positions. Regardless of this, at least two locations (the bearing oil passage holes 72 located on the upper end side and the lower end side in FIG. 4) communicate with each other. Note that a plurality of lubricating oil holes 73 are formed in the circumferential direction (10 in this embodiment) as indicated by solid and broken lines. Further, the outer race 36 shown by a broken line is formed with a plurality of outer race oil passage grooves 67 (4 in the present embodiment at equal angular intervals) penetrating in the radial direction, each of which is a bearing of the second rear race 60. The outer periphery of the oil passage hole 72 is communicated.

  Since the second rear race 60 and the end bearing 42 can rotate relative to each other, the hole position of the bearing oil passage hole 72 of the second rear race 60 and the hole position of the lubricating oil hole 73 of the end bearing 42 are mutually different. Relative movement in the circumferential direction at any time due to relative rotation of. However, in the present embodiment, a plurality of bearing oil passage holes 72 and lubricating oil holes 73 are formed in the circumferential direction, so that no matter what the phase relationship between the second rear race 60 and the end bearing 42 is. The bearing oil passage hole 72 and the lubricating oil hole 73 are set so as to always communicate with each other. Similarly, since the second rear race 60 and the outer race 36 are rotatable relative to each other, the hole position of the bearing oil passage hole 72 of the second rear race 60 and the groove position of the outer race oil passage groove 67 of the outer race 36 are different from each other. , Relative movement in the circumferential direction at any time by mutual relative rotation. However, in this embodiment, a plurality of bearing oil passage holes 72 and outer race oil passage grooves 67 are formed in the circumferential direction, and the outer circumference side of the bearing oil passage holes 72 is formed with a wide hole width in the circumferential direction. Therefore, the bearing oil passage hole 72 and the outer race oil passage groove 67 are set to always communicate with each other regardless of the phase relationship between the bearing oil passage hole 72 and the outer race oil passage groove 67. .

  Here, for example, when the lockup clutch 16 of the torque converter 10 is engaged, oil is supplied from a gap formed between the input shaft 28 and the fixed shaft 26. This oil lubricates the inside of the one-way clutch 18 from the lubricating oil hole 73 of the end bearing 42 through the bearing oil passage hole 71 of the second front race 54. The oil is supplied from the lubricating oil hole 73 of the end bearing 42 located on the second rear race 60 side to the bearing oil passage hole 72 of the second rear race 60. Further, since the bearing oil passage hole 72 communicates with the outer race oil passage groove 67 of the outer race 36, the oil reaches the bearing oil passage groove 74 of the second rear race 60 through the outer race oil passage groove 67. The oil that has reached the bearing oil passage groove 74 passes through this groove and is supplied into the torque converter 10.

  As described above, according to the stator support device 34 of the torque converter of the present embodiment, the second rear race 60 is not stopped, so that complicated processing such as providing a key on the stator wheel 20b is not performed. Cost can be suppressed. Further, since the gap 75 is formed between the inner peripheral portion of the stator wheel 20b and the outer peripheral portion of the second rear race 60, sliding wear between these members can be prevented.

  Further, according to the stator support device 34 of the torque converter of the present embodiment, the stepping portion 64 is formed on the outer peripheral portion of the outer race 36 and the inner side surface of the stator wheel 20b is formed radially inward. Since the side walls of the stoppers 66 are in contact with each other, when a thrust load in the axial direction is applied to the stator wheel 20b, the thrust load is directly transmitted to the outer race 36 via the contact portion. Thus, the transmission of the thrust load to the outer periphery of the second rear race 60 is prevented. As a result, deformation of the outer peripheral portion of the second rear race 60 is prevented.

  Further, according to the stator support device 34 of the torque converter of the present embodiment, a plurality of bearing oil passage holes 72 are formed on the side surface of the second rear race 60 and a plurality of bearing oil passage grooves 74 are formed on the outer peripheral portion. Therefore, even if the second rear race 60 is freely rotated, the lubricating oil hole 73 and the bearing oil passage hole 72 that are always formed in the end bearing 42 are communicated with each other and the outer race 36 is formed. The outer race oil passage groove 67 and the bearing race oil passage hole 72 communicate with each other, and stable oil supply becomes possible.

  As mentioned above, although the Example of this invention was described in detail based on drawing, this invention is applied also in another aspect.

  For example, the bearing oil passage holes 72 of the above-described embodiment are formed in the second rear race 60 in a T-shape, but the shape and number of these holes are not limited and are within a consistent range. It can be changed freely. That is, the lubricating oil hole 73 and the outer race oil passage groove 67 can be freely changed within a range in which the lubricating oil hole 73 and the outer race oil passage groove 67 communicate with the bearing oil passage hole 72 efficiently. Similarly, the shape and number of the outer race oil passage groove 67, the lubricating oil hole 73, and the bearing oil passage groove 74 in the above-described embodiment can be freely changed within a range in which these oil holes and oil grooves are efficiently communicated. be able to.

  In the above-described embodiment, the stator wheel 20b and the outer race 36 are integrated with each other by serration press-fitting. In the range where the outer race 36 is integrated, it can be freely changed.

  The above description is only an embodiment, and the present invention can be implemented in variously modified and improved forms based on the knowledge of those skilled in the art.

It is sectional drawing explaining the structure of the torque converter which is one Example of this invention. It is principal part sectional drawing for demonstrating the stator support apparatus which supports the stator of FIG. FIG. 3 is a component diagram for explaining the shape of the rear race of FIG. 2. FIG. 3 is a layout diagram showing a positional relationship among a stator, a rear race, an outer race, and a snap ring, and corresponds to an arrow view seen from the direction of arrow A in FIG. 2.

Explanation of symbols

10: Torque converter 18: One-way clutch 20b: Stator wheel 34: Stator support device 36: Outer race 38: Inner race 60: Rear race (bearing race) 64: Stepped portion 66: Stopper (projection) 67: Outer race oil passage groove 72: Bearing oil passage hole 73: Lubricating oil hole 74: Bearing oil passage groove 75, 77: Clearance

Claims (3)

Between the outer race of the one-way clutch disposed on the inner periphery of the stator wheel of the torque converter, the inner race of the one-way clutch connected to the outer periphery of the non-rotating member so as not to be relatively rotatable, and between the outer race and the inner race A stator support device for a torque converter having an end bearing interposed between the outer race and a bearing race disposed on a side surface of the outer race,
The bearing race is supported so as to be rotatable relative to the outer race,
A gap is formed between the bearing race and the stator wheel ,
A plurality of bearing oil passage holes are formed in the circumferential direction on the side surfaces of the bearing races as appropriate in communication with the lubricating oil holes formed in the end bearings. The lubricating oil supplied to the bearing oil passage holes is The bearing oil passage holes communicate with the outer race oil passage grooves formed in the circumferential direction in the outer race as appropriate, so that the bearing oil passage holes are supplied to the bearing oil passage grooves formed in the outer peripheral portion of the bearing race. ,
A stator support for a torque converter , wherein the axial length of the gap formed between the stator wheel and the bearing race is set substantially equal to the groove depth of the outer race oil passage groove. apparatus. The inner peripheral portion of the stator wheel and the outer peripheral portion of the outer race are fitted by press-fitting,
The side wall of the stepped portion formed on the outer peripheral portion of the outer race and the side wall of the protruding portion formed radially inward from the inner peripheral surface of the stator wheel are in contact with each other. 2. The stator support device for a torque converter according to claim 1, wherein the stator support device is a torque converter. 3. The stator support device for a torque converter according to claim 1, wherein an outer peripheral side of the bearing oil passage hole is formed with a wide hole width in a circumferential direction .

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